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EP0419684A1 - Element de frottement dans un couple de frottement - Google Patents

Element de frottement dans un couple de frottement Download PDF

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Publication number
EP0419684A1
EP0419684A1 EP90906433A EP90906433A EP0419684A1 EP 0419684 A1 EP0419684 A1 EP 0419684A1 EP 90906433 A EP90906433 A EP 90906433A EP 90906433 A EP90906433 A EP 90906433A EP 0419684 A1 EP0419684 A1 EP 0419684A1
Authority
EP
European Patent Office
Prior art keywords
friction element
friction
element according
zone
frame
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP90906433A
Other languages
German (de)
English (en)
Other versions
EP0419684A4 (en
Inventor
Vladimir Vladimirovich Morgun
Sergei Stepanovich Lebedenko
Stepan Ivanovich Kravchun
Viktor Petrovich Khupovka
Vyacheslav Alexandrovich Boguslaev
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ZAPOROZHKOE PROIZVODSTVENNOE OBIEDINENIE "MOTOROSTROITEL"
ZAPOROZHSKY AVTOMOBILNY ZAVOD 'KOMMUNAR' (PROIZVODSTVENNOE OBIEDINENIE 'AVTOZAZ')
Original Assignee
ZAPOROZHKOE PROIZVODSTVENNOE OBIEDINENIE "MOTOROSTROITEL"
ZAPOROZHSKY AVTOMOBILNY ZAVOD 'KOMMUNAR' (PROIZVODSTVENNOE OBIEDINENIE 'AVTOZAZ')
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from SU894672584A external-priority patent/RU1775570C/ru
Application filed by ZAPOROZHKOE PROIZVODSTVENNOE OBIEDINENIE "MOTOROSTROITEL", ZAPOROZHSKY AVTOMOBILNY ZAVOD 'KOMMUNAR' (PROIZVODSTVENNOE OBIEDINENIE 'AVTOZAZ') filed Critical ZAPOROZHKOE PROIZVODSTVENNOE OBIEDINENIE "MOTOROSTROITEL"
Publication of EP0419684A1 publication Critical patent/EP0419684A1/fr
Publication of EP0419684A4 publication Critical patent/EP0419684A4/de
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D69/00—Friction linings; Attachment thereof; Selection of coacting friction substances or surfaces
    • F16D69/02—Composition of linings ; Methods of manufacturing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/60—Clutching elements
    • F16D13/64—Clutch-plates; Clutch-lamellae
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/72—Features relating to cooling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/0006—Noise or vibration control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/10—Drums for externally- or internally-engaging brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/12—Discs; Drums for disc brakes
    • F16D65/127—Discs; Drums for disc brakes characterised by properties of the disc surface; Discs lined with friction material
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/78—Features relating to cooling
    • F16D65/84—Features relating to cooling for disc brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D69/00—Friction linings; Attachment thereof; Selection of coacting friction substances or surfaces
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D69/00—Friction linings; Attachment thereof; Selection of coacting friction substances or surfaces
    • F16D2069/002—Combination of different friction materials
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D69/00—Friction linings; Attachment thereof; Selection of coacting friction substances or surfaces
    • F16D2069/004—Profiled friction surfaces, e.g. grooves, dimples

Definitions

  • the invention relates to friction pairings of machine parts and relates in particular to a friction element of a friction pairing.
  • a friction disc (US, A, 3773153) which is made up of a composite, namely its outer parts are made of steel, but the core is made of corrugated aluminum plates.
  • reinforcement sleeves leads to an increase in the cost of materials and the weight of the construction and, on the other hand, does not guarantee the optimum load-bearing capacity of the friction surface as well as the excess of the connection and the resistance to loosening, which in the end has a negative effect on the service life of the friction disc.
  • a friction element of a friction pairing namely a brake disc
  • SU a friction element of a friction pairing
  • a brake disc which has a three-dimensional framework, which is accommodated in a matrix, which is made of a material with a high coefficient of thermal conductivity.
  • Coating the friction surfaces of the disc from a wear-resistant material does not result in their optimal load-bearing capacity.
  • the invention has for its object to provide such a friction element of a friction pair, the structure of which ensures a uniform resistance of different zones of the friction surface against destruction during operation while ensuring their optimal load-bearing capacity.
  • a friction element of a friction pairing which contains a three-dimensional framework, which is accommodated in a matrix made of a material with a high coefficient of thermal conductivity, and a friction surface
  • the framework is made of a wear-resistant material and at least in the zone of Arranged friction surface, which has a regular microrelief, which is formed by the matrix and the front end of the framework projecting above its surface.
  • Such parts in the friction element according to the invention are the parts protruding over the matrix, and since they are arranged discretely and regularly on the friction surface, the latter proves to be one which essentially corresponds to the actual surface area of the contact surfaces. As a result, only a minimal amount of wear-resistant material is consumed, which has a positive effect on the cost of manufacturing the friction element.
  • Such a design of the friction element also increases the overall rigidity and strength of the structure and reduces its mass.
  • the friction surface of the friction element is partially formed by the matrix, which is made of a material with a high coefficient of thermal conductivity, the heat dissipation from the friction surface is improved, thereby increasing the useful life of the product as a whole.
  • the scaffold can advantageously be designed in the form of a cell structure.
  • the regular microrelief on the friction surface can preferably have a cell shape which contributes in the best way to increasing the working capacity and the service life of the friction element.
  • Such an embodiment of the friction element can preferably be used as a brake drum of a motor vehicle, as a thrust bearing and the like.
  • the area of the end face of the scaffolding projecting beyond the matrix decreases proportionally in the direction from the zone of the maximum load to the zone of the minimum load.
  • the area of the end face can be changed by changing the cell size and / or the wall thickness of the cell structure and / or the arrangement density of the cells.
  • the strengthening of the friction surface of the friction element in the zone of the maximum load which can be achieved due to the increased surface area of the end face of the frame, has the advantage that the wear of this zone slows down during operation. This creates the conditions for uniform wear of the friction surface, which experiences uneven thermomechanical stresses, which contributes to extending the useful life of the product.
  • the framework of the friction element can preferably be made from a more wear-resistant material in the zone of the maximum load than in the zone of the minimum load.
  • the micro-relief on one surface can preferably be configured differently from the regular micro-relief on the other surface in terms of configuration.
  • Such training counteracts the occurrence of natural vibrations, a form of resonance of the wave, the clinking and beeping.
  • Plates can preferably be arranged between the cells of the scaffold.
  • the plates can also be used to prevent the above-mentioned shortcomings.
  • the framework of the friction element is made from a corrugated band.
  • the band must be wound in a helical line.
  • Such a design prevents the possible packaging of the belts and thus contributes to the high-quality shaping of the friction element.
  • the scaffold consists of at least two parts arranged in the same axis with rewinding in opposite directions.
  • Such a design is very beneficial for the compensation of the axial component and the damping of the vibration and thus contributes to increasing the life of the friction element.
  • the corrugated band must be wound up in a spiral shape with an incline that increases in the direction of increase in the radius of the spiral.
  • Such a winding has the advantage that the friction material of the belts is arranged in accordance with the thermomechanical stresses acting on the friction surface, i.e. denser in the zone of maximum load of the product and less dense in the zone of minimum load, which favors a uniform resistance to destruction of the friction surface.
  • corrugated band with an incline and a height which increases over its length in the direction of enlargement of the radius of the spiral serves the same purpose.
  • the belts forming the framework can preferably be provided with corrugations.
  • the corrugations enlarge the surface of the framework and increase its rigidity and strength.
  • the perforation reinforces the anchor effect of the fastening of the bands in the matrix and improves the heat dissipation, which in the end increases the service life of the friction element.
  • the winding direction of the spiral can preferably be with the direction of rotation of the friction element, e.g. a brake disc, so that compressive stresses act on them during operation.
  • the friction element e.g. a brake disc
  • Figure 1 shows a brake disc according to the invention.
  • Figure 2 shows the brake disc in plan.
  • FIG. 4 shows a scaffold in the form of a cell structure in axonometry
  • FIG. 6 shows a fragment of a friction element, which illustrates the presence of a microrelief on the friction surface
  • FIG. 10 shows a fragment of a friction element with a framework in the form of a spatial network in section
  • FIG. 11 shows a brake disk with changing arrangement density of the cells of the frame on the friction surface in the plan view
  • FIG. 13 shows a brake disc, on the mutually opposite friction surfaces of which the scaffold cells are designed in different configurations
  • FIG. 14 shows the brake disc shown in FIG. 13 in a view from the left
  • FIG. 15 shows the brake disc shown in FIG. 13 in a view from the right
  • FIG. 16 shows a brake disc with a framework consisting of a corrugated band
  • Figure 18 shows a scaffold made up of several pairs of tape windings which have an opposite winding direction
  • Fig. 19 shows a scaffold which is designed in the form of a corrugated band which is wound into a flat spiral
  • a friction element of a friction pairing contains a three-dimensional framework 1 (FIGS. 1, 2, 3, 4) which is accommodated in a matrix 2 made of a material with a high coefficient of thermal conductivity.
  • the scaffold 1 can be in the form of honeycombs (Fig. 2, 4, 5), a grid (Fig. 7, 8), a spatial network (Fig. 9, 10) and the like made of a material that has a higher strength and heat wear resistance as the heat-dissipating material of the matrix 2, which fills this framework.
  • the frame 1 can be made of steel and the matrix 2 of an aluminum alloy.
  • the framework 1 and the matrix 2 are each made of alloys based on Mo, W and copper.
  • the frame 1 has a coating (FIG. 3) which consists of a material which is compatible with the material of the frame 1 and the matrix 2 and has good thermal conductivity.
  • Copper can preferably be used as the coating for the framework 1 based on Fe and for the matrix 2 based on Al.
  • the scaffold 1 partially protrudes with its end face over the matrix 2 and, together with the latter, forms a friction surface 4 with discretely arranged sections of a wear-resistant material, via which contact occurs during the operation of the friction pairing.
  • the frame 1 can be accommodated not only in the zone of the friction surface 4, but also in the entire volume of the friction element.
  • the area of the part of the frame 1 on the friction surface 4 makes up from 3 to 70% in relation to the total friction surface 4, which corresponds to the actual contact surface area.
  • the friction element can preferably be produced in the form of a reinforced casting.
  • It can be shaped by sintering or dusting.
  • the friction surface 4 is treated with the aim of giving it the final shape, the dimensions and the roughness.
  • the friction surface 4 corresponds to a surface with a completely regular microrelief, for example with a hexagonal microrelief (FIGS. 2, 5, 6, 11, 12).
  • an embodiment is most favorable in which the end face content of the scaffold 1 changes from the zone of the maximum load to the zone of the minimum load (FIGS. 2, 11, 12, 13, 14, 15, 19) proportionally reduced.
  • the wear surface of the friction disks has a hyperbolic shape and that the deformation and wear decrease when the point of the conjugation surface is removed from the axis of rotation due to the reduction in pressure.
  • the end face content of the scaffold 1 can be changed by changing the size of the cells 5 of the scaffold 1 and / or the thickness of its walls 6 and / or the arrangement density of the cells 5.
  • each of them is reinforced by a framework 1 which has different configurations of the cells 5 (for example a square and a hexagonal) which have different contours of the regular microrelief ( 14, 15) form, or one additionally reinforces the friction surfaces 4 of the disk by plates 7 (FIG. 12), which are arranged radially distributed between the cells 5 of the frame 1, which eliminates vibrations.
  • a framework 1 which has different configurations of the cells 5 (for example a square and a hexagonal) which have different contours of the regular microrelief ( 14, 15) form, or one additionally reinforces the friction surfaces 4 of the disk by plates 7 (FIG. 12), which are arranged radially distributed between the cells 5 of the frame 1, which eliminates vibrations.
  • the framework 1 can be made of different materials with regard to the wear resistance. In the zone of maximum load, materials are to be used that have better physical and mechanical properties than in the zones of minimum load.
  • the frame 1 can be made from a corrugated band 8 (FIG. 16).
  • the corrugated band 8 is to be wound up helically, the turns of a flat band 9 being arranged between the turns of the spiral line.
  • the bands 8, 9 are oriented with their end faces towards the friction surface 4 of the friction element, so that a regular microrelief is formed on the latter, the geometry of which is determined by the geometry of the cells 5 formed by the bands 8, 9.
  • such a scaffold 1 is made of at least two parts arranged in the same axis with oppositely directed wind-up (FIGS. 17, 18).
  • the corrugated band 8 is wound in a spiral line shape, the slope of the spiral increasing in the direction of enlargement of its radius (FIG. 19) in accordance with the arrangement of the load zones of the friction surface 4 and the slope and height of the beads along the length of the spiral in Increase the direction of enlargement of their radius.
  • the winding direction of the spiral coincides with the direction of rotation of the friction element.
  • turns of the corrugated band 9 are arranged.
  • the strips 8, 9 are oriented with their end faces towards the friction surface 4, so that a microrelief is formed on the latter, the geometry of which is also determined by the geometry of the cells 5 formed by the strips 8, 9.
  • the friction material is arranged on the friction surface 4 depending on its load character, namely more densely in the zone of the maximum load than in the zone of the minimum load.
  • corrugations 11 are also provided on the surface of the belts 8, 9.
  • the corrugations enlarge the surface of the reinforcement structure 1 and thus increase its rigidity and strength.
  • the coating 3 of the framework 1 which has a high thermal conductivity and is well compatible with the heat-dissipating matrix material, favors this process because the coating 3 excludes the thermal barrier between the framework 1 and the matrix 2. As a result, the heat is distributed in the volume of the friction element.
  • the friction element according to the invention is also suitable as a support structure, for example as a bearing sleeve with a friction surface which is designed and functions analogously to that described.
  • the invention can be used in brake systems, in particular in passenger cars, in clutch disks, in various support structures and the like.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)
  • Nitrogen And Oxygen Or Sulfur-Condensed Heterocyclic Ring Systems (AREA)

Abstract

L'élément de frottement décrit est composé d'une carcasse tridimensionnelle (1) situé dans une matrice (2) dans une zone d'une surface de frottement (4). La carcasse est réalisée en un matériau résistant à l'usure, et la matrice (2) est constituée par un matériau ayant un coefficient de conductivité thermique élevée. La carcasse (1) a une structure cellulaire composée de nids d'abeilles, une bande ondulée ou analogues. La carcasse (1) fait saillie au-dessus de la surface de la matrice (2) et forme, avec cette dernière, une surface de frottement (4) avec un microrelief régulier. La superficie de la carcasse (1), qui fait saillie au-dessus de la matrice (2), décroît proportionnellement depuis la zone de sa charge maximale vers la zone de sa charge minimale. L'invention peut être utilisée dans des dispositifs de freinage, en particulier dans des disques de frein pour véhicules légers, des plateaux d'embrayage et analogues.
EP19900906433 1989-04-04 1990-04-04 Friction element of a friction pair Pending EP0419684A4 (en)

Applications Claiming Priority (8)

Application Number Priority Date Filing Date Title
SU894672584A RU1775570C (ru) 1989-04-04 1989-04-04 Фрикционный элемент
SU4672584 1989-04-04
SU4716748 1989-07-10
SU4716748 1989-07-10
SU4766345 1989-09-15
SU4766345 1989-09-15
SU4784102 1990-01-18
SU4784102 1990-01-18

Publications (2)

Publication Number Publication Date
EP0419684A1 true EP0419684A1 (fr) 1991-04-03
EP0419684A4 EP0419684A4 (en) 1991-10-02

Family

ID=27484929

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19900906433 Pending EP0419684A4 (en) 1989-04-04 1990-04-04 Friction element of a friction pair

Country Status (5)

Country Link
US (1) US5163526A (fr)
EP (1) EP0419684A4 (fr)
JP (1) JPH03505249A (fr)
HU (1) HUT59209A (fr)
WO (1) WO1990012219A1 (fr)

Cited By (5)

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Publication number Priority date Publication date Assignee Title
EP0525439A1 (fr) * 1991-07-29 1993-02-03 Linde Aktiengesellschaft Disque de frein
WO1995001520A1 (fr) * 1993-07-02 1995-01-12 Knorr-Bremse Ag Disque de frein pour freins a disque
EP0687829A1 (fr) * 1994-06-17 1995-12-20 Wagner Electric Corporation Matériau de friction renforcé
WO2000032335A1 (fr) * 1998-12-03 2000-06-08 Otto Junker Gmbh Piece moulee composite et son procede de fabrication
CN109404432A (zh) * 2018-12-28 2019-03-01 东北大学 一种金属挠性膜盘联轴节

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ES2211928T3 (es) * 1995-11-24 2004-07-16 Deutsches Zentrum Fur Luft- Und Raumfahrt E.V Disco de freno.
US5680921A (en) * 1996-02-07 1997-10-28 Borg-Warner Automotive, Inc. Transmission band assembly
DE19622520C1 (de) * 1996-06-05 1997-11-27 Ebern Fahrzeugtech Gmbh Innenbacken-Trommelbremse
ATE215189T1 (de) * 1996-12-13 2002-04-15 Tmd Friction Gmbh Teilbelagscheibenbremse und bremsbacke
US5979615A (en) * 1997-11-06 1999-11-09 Otis Elevator Company Carbon--carbon composite elevator safety brakes
US6371261B1 (en) 1997-11-06 2002-04-16 Otis Elevator Company Molybdenum alloy elevator safety brakes
WO1999028646A2 (fr) * 1997-11-27 1999-06-10 Continental Teves Ag & Co. Ohg Disque de frein, notamment pour vehicules automobiles
EP1418065A1 (fr) * 2002-11-06 2004-05-12 ISCA S.p.A Roue avec face de frottement en matériau à haut coéfficient de friction
DE10324186A1 (de) * 2003-05-28 2004-12-16 Volkswagen Ag Bremsscheibe für ein Fahrzeug
US8978842B2 (en) * 2011-11-24 2015-03-17 Shimano Inc. Bicycle disc brake rotor
CN102853012B (zh) * 2012-09-04 2015-12-09 浙江大学宁波理工学院 一种具有仿生结构的刹车片及其制备方法
CN105349097B (zh) * 2015-12-10 2018-04-27 吉林大学 一种结构仿生摩擦材料及其制造方法
US9982730B2 (en) * 2016-06-21 2018-05-29 Nissan North America, Inc. Brake pad
US9982729B2 (en) * 2016-06-21 2018-05-29 Nissan North America, Inc. Brake pad
CN108386465A (zh) * 2018-05-07 2018-08-10 安徽工业大学 一种具有仿生表面的汽车制动盘
DE102019205570A1 (de) * 2019-04-17 2020-10-22 Zf Friedrichshafen Ag Kühlölleitelement sowie Antriebsstrang mit diesem
CN111177846B (zh) * 2019-12-11 2021-03-09 上海卫星工程研究所 快速创建大型蜂窝板内埋框架的三维建模方法
AT17380U1 (de) * 2021-02-10 2022-02-15 Plansee Se Bremsscheibe für eine scheibenbremse

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0525439A1 (fr) * 1991-07-29 1993-02-03 Linde Aktiengesellschaft Disque de frein
WO1995001520A1 (fr) * 1993-07-02 1995-01-12 Knorr-Bremse Ag Disque de frein pour freins a disque
EP0687829A1 (fr) * 1994-06-17 1995-12-20 Wagner Electric Corporation Matériau de friction renforcé
KR100323798B1 (ko) * 1994-06-17 2002-07-02 다이안 케이.슈마허 보강된마찰재와그제조방법
WO2000032335A1 (fr) * 1998-12-03 2000-06-08 Otto Junker Gmbh Piece moulee composite et son procede de fabrication
CN109404432A (zh) * 2018-12-28 2019-03-01 东北大学 一种金属挠性膜盘联轴节

Also Published As

Publication number Publication date
HU903411D0 (en) 1991-08-28
JPH03505249A (ja) 1991-11-14
US5163526A (en) 1992-11-17
HUT59209A (en) 1992-04-28
EP0419684A4 (en) 1991-10-02
WO1990012219A1 (fr) 1990-10-18

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